Sealing structure for fishing reel

ABSTRACT

Sealing structure has a friction disk having a spindle-form boss portion, a cover member, and a seal member, in a lever-drag type dual-bearing reel. Cover member has a through-hole situated encompassing the boss portion, and is a component that is rotatable relative to friction disk. The seal member, which is a component made of an elastic substance, is for sealing a clearance between the boss portion and the cover member, and has an cylindrical portion made of an elastic substance and mountable on the boss portion, and a sealing portion formed integrally on the outer circumferential surface of the cylindrical portion and tapering toward the through-hole. A distal edge of the sealing portion is for contacting a contact surface in through-hole. The present invention provides a structure for sealing a spindle-form first member and, disposed about the outer periphery thereof, a second member, to seal while controlling impairment in rotational performance, without having to use components or space for fastening.

This is a divisional application of Ser. No. 10/042,183, filed on Jan.11, 2002, now U.S. Pat. No. 6,712,301, and claiming right of priority toJapanese Patent Application No. 2001-015596, filed on Jan. 24, 2001.Certified copies of the priority documents have been filed in the Ser.No. 10/042,183 application.

BACKGROUND OF THE INVENTION

1. Field of the Invention

This invention generally relates to sealing structures. Morespecifically, the present invention relates fishing-reel sealingstructures that seal between a spindle-form first member and a secondmember disposed about the outer periphery of the first member in fishingreels.

2. Background Information

Because fishing reels such as spinning reels and dual-bearing reels areused in environments where they are constantly splashed with water,sealing structures are employed in fishing-reel applications forpreventing water from encroaching interiorly. In particular, rings andoil-seals have been in widespread use conventionally for sealing inbetween relatively rotatable shaft members and their encompassingmembers. O-rings and oil-seals are used, for example, on the outer sideof handle-carrying bearings in spinning reels or in between covermembers and the spool shafts in dual-bearing reels.

In conventional O-ring based sealing structures, the O-rings areslightly squashed in order to form a seal. This means that thecontacting surface area of the O-rings is extensive, and in particular,where the two members are relatively rotatable, the O-rings make therotational resistance large, which tends to impair the rotationalperformance.

Oil seals are generally composed of a lip made of rubber, and ashape-retaining backing member made of metal. Accordingly, with oil-sealbased sealing structures, because the contacting part is a peaked lipshape, it is comparatively easy to curb degradation in rotationalperformance. However, oil seals cannot be extended/contracted due to thebacking member made of metal, and therefore fastening members and aspace for fixing the oil-seal are necessary, which increases the axialspace required to accommodate the oil seals.

In view of the above, there exists a need for sealing structure whichovercomes the above mentioned problems in the prior art. This inventionaddresses this need in the prior art as well as other needs, which willbecome apparent to those skilled in the art from this disclosure.

SUMMARY OF THE INVENTION

An object of the present invention is to provide a structure for sealinga spindle-form first member and a second member disposed about the outerperiphery thereof, to seal without having to use components or space forfastening, while curbing rotational-performance impairment.

A fishing-reel sealing structure having is furnished with afishing-reel, spindle-form first member, a second member, and a sealmember. The second member has an inner peripheral surface disposed aboutthe first member outer-peripherally, and is rotatable relative to thefirst member. The seal member, a component made of an elastic substance,seals the clearance between the two members; and has: anelastic-manufacture cylindrical portion mountable on the first member;and a sealing portion formed integrally on the outer circumferentialsurface of the cylindrical portion, and tapering toward the innerperipheral surface of, and whose distal edge is for contacting on, thesecond member.

In this sealing structure, the cylindrical portion of the seal membermade of an elastic substance is fitted to the spindle-form first member,and bringing the tapered sealing portion into contact with the innercircumferential surface of the second member seals the clearance betweenthe two members. Herein, the fact that the tapered sealing portion isbrought into contact with the second member to seal the clearancebetween the two members means that the surface area of the places incontact is smaller, making degradation in rotational performanceunlikely. Likewise, that fact that, like O-rings, the seal member isentirely made of an elastic substance makes it extendable/contractible,which means that, for example, it may be fastened to the first membersimply by fitting its cylindrical portion into a groove. Components andspace for fastening the seal member are therefore made unnecessary.

Preferably, an annular groove is formed in a first-member outercircumferential surface that opposes the second member, and thecylindrical portion is fitted into the annular groove. In this case, theseal member may be fastened to the first member just by stretching thecylindrical portion and fitting it into the first member, and set thatway shifting axially to mount the seal member in the annular groove.

Preferably, the part of the sealing portion for contacting the secondmember is a lip inclined heading outward of the first member. In thiscase, the fact that the sealing portion is a lip inclined headingoutward of the first member means that when mounting the first memberfrom without, the second member will not reverse even though it contactsthe sealing portion. Moreover, since the fore end of the sealing portionis oriented outward, though liquids enter from without, the liquids arenot likely to encroach interiorly.

Preferably, the first member is a constituent of a lever-drag mechanismin a lever-drag-type dual-bearing reel having a line-winding spool, andtherein is a stationary component immovable in the axial direction ofthe spool; and the second member is a constituent of the lever-dragmechanism that is rotatable relative to the first member, and therein isa shifting member for shifting in the axial direction of the spool. Inthis case, utilizing the spool member also in a lever-drag mechanismcurbs degradation in rotational performance when the spool spins freely.

Preferably, the first member is a drag disk capable of braking thespool, and rotates linked to a spool shaft passing through the spoolcenter; and the second member is a cover member for covering the dragdisk, and rotates linked to the spool and meanwhile shifts in the axialdirection together with the spool and the spool shaft. In this case,fluctuations in drag force may be controlled by sealing the clearancebetween the cover member and the drag disk.

Preferably, the drag disk has a boss portion passing centrally throughthe cover member; the seal member is fitted to the boss portion; and acontact face for the seal to contact and a relief face the seal does notcontact are formed, ranged in the spool axial direction, superficiallyon the inner rim of the cover member. In this case, relative axialmovement between the drag disk and the cover member brings the sealingportion of the seal member into contact with/parts it from the covermember. This allows for specific conditions whereby the sealing portiondoes not contact the cover member so as not to impair the rotationalperformance.

Preferably, the sealing portion of the sealing member: parts away fromthe cover member to oppose the relief face, when the drag disk in itsbrake-release state parts away from the spool; and comes into oppositionwith, to contact on, the contact face when the drag disk in its brakingstate contacts the spool. In this case, the fact that the during thebrake-release state the sealing portion is opposite the relief face,where it is parted off the cover member, means it does not impairrotational performance when the spool spins freely, and lets fishingline be reeled out agilely though a seal member is installed. Likewise,during the braking state, the sealing portion seals positively by cominginto contact with the contact face of the cover member.

Preferably, the spool has a bobbin-trunk portion, and flange portionsarranged on either end of the bobbin-trunk portion; and the outerdiameter of the sealing portion is 8% or more and 50% or less of theouter diameter the flange portions. In this case, the fact that theouter diameter of the sealing portion is 50% or less that the outerdiameter of the flange portions means that the contacting surface areaof the sealing-member sealing portion is sufficiently small with respectto the spool, which curbs degradation in rotational performance thoughthe seal member is brought into contact with the second member.Likewise, the fact that the outer diameter of the sealing portion is 8%or more lets strength of the spool shaft be sustained with the sealmember fitted into a first member mounted encompassing the spool shaft.

Preferably, the first member is a handle spindle fitted detachably andreattachably to a spinning-reel master-gear shaft; and the second memberis a reel body rotatively carrying the master-gear shaft. In this case,impairment in rotational performance of the spinning-reel handle may becontrolled; meanwhile in either case where the handle is fitted onthrough the left or the right, sealing either end of the master gearshaft may be accomplished with a single seal member.

A fishing-reel sealing structure is furnished with a fishing-reel,spindle-form first member, a second member, and a seal member. Thesecond member has an inner peripheral surface disposed about the firstmember outer-peripherally, and is rotatable relative to the firstmember. The seal member, a component made of an elastic substance, sealsthe clearance between the two members, and has: an elastic-manufacturecylindrical portion mountable on the second member; and a sealingportion formed integrally on the inner circumferential surface of thecylindrical portion and tapering toward the outer circumferentialsurface of the first member, and whose distal edge is for contacting onthe first member.

In this sealing structure, the cylindrical portion of the seal membermade of an elastic substance is fitted to the second member and bringingthe tapered sealing portion into contact with the outer circumferentialsurface of the first member seals the clearance between the two members.Herein, the fact that the tapered sealing portion is brought intocontact with the first member to seal the clearance between the twomembers means that the surface area of the contacting places is smaller,making degradation in rotational performance unlikely. Likewise, thatfact that, like O-rings, the seal member is entirely made of an elasticsubstance makes it extendable/contractible, which means that, forexample, it may be fastened to the second member simply by fitting itscylindrical portion into a groove. Components and space for fasteningthe seal member are therefore made unnecessary.

These and other objects, features, aspects and advantages of the presentinvention will become apparent to those skilled in the art from thefollowing detailed description, which, taken in conjunction with theannexed drawings, discloses a preferred embodiment of the presentinvention.

BRIEF DESCRIPTION OF THE DRAWINGS

Referring now to the attached drawings which form a part of thisoriginal disclosure:

FIG. 1 is a cross-sectional view of a lever-drag reel in accordance withthe first embodiment of the present invention;

FIG. 1 is a side view of the lever-drag reel in accordance with thefirst embodiment;

FIG. 3 is an enlarged cross-sectional view of sealing section for covermember;

FIG. 4 is a left-side view of a spinning reel in accordance with thesecond embodiment of the present invention;

FIG. 5 is a left-side cross-sectional view in accordance with the secondembodiment;

FIG. 6 is an exploded perspective view of reel unit in accordance withthe second embodiment;

FIG. 7 is a partial cross-sectional view of the handle assembly and thereel body viewed through the line VII—VII in FIG. 5;

FIG. 8 is an enlarged cross-sectional view of sealing section for handleshaft; and

FIG. 9 is a partial cross-sectional view of spool and rotor centerportion.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1

As seen in FIG. 1, a dual-bearing reel into which Embodiment 1 of thepresent invention is adapted is a lever-drag reel, and is furnishedwith: a cylindrical reel unit 1; a spool shaft 2, rotatively fitted inthe central portion of the reel unit 1; a spool 3, carried rotativelyyet axially immovably on the spool shaft 2; and a handle 4, disposedsideways on the reel unit 1. Likewise, within the reel unit 1 interior,the lever-drag reel is furnished with: a torque-transmitting mechanism 6that transmits torque from the handle 4 to the spool 3; a lever-dragmechanism that brakes rotation of the spool 3 in the line-reel-outdirection; a spool locking mechanism 8 that locks the spool 3, and aanti-reverse mechanism 9 that controls rotation of the lever-dragmechanism 7 in the line-reel-out direction.

Reel Body Configuration

The reel unit 1 has: a left/right pair of plate-shaped side plates 10,11 made of metal; and a perforated cylindrical reel unit 12, made ofmetal, to either end of which the side plates 10, 11 are joinedcoaxially by spigot joints and fastened by a plurality of fixing screws13. Harness lugs 14 of a pair, used for supporting the reel with thebody, are mounted in between the side plates 10, 11 and the reel unit12. The approximately central portions of the side plates 10, 11rotatively support either end of the spool shaft 2. A cylindricalbearing accommodating portion 10 a that protrudes inward is formed inthe central portion of the inside face of the left side plate 10. A boss11 a protruding axially outward is formed in the central portion of theright side plate 11 (handle 4 side) for supporting the spool shaft 2;and on the periphery of the boss 11 a, a thick-walled, disk-shapedbearing block 15 for mounting the handle shaft 5 of the handle 4 isscrewed fast. The under portion of the reel unit 12 is provided with arod attachment part 19 for mounting the reel onto a fishing rod.

Configuration of Spool and Spool Shaft Environs

By a pair of left and right bearings 31 a, 31 b disposed at either end,the spool shaft 2 is rotatively supported in the side plates 10 and 11on the reel unit 1. Also, spaced axially inward thereof are two bearings32 a, 32 b disposed at either end of the spool 3, by which the spool 3is rotatively supported. The bearing 31 a on the left side isaccommodated by the bearing accommodating portion 10 a formed on theleft side plate 10. The bearing 31 b on the right side is mounted in theboss 11 a formed on the right side plate 11. The components of adrag-shifting mechanism 38 (described later) for the lever-dragmechanism 7 adjoins the right side of the bearing 31 b outer race on theright end of the spool shaft 2. Additionally, a pinion gear 17(described later) for the rotation transmission mechanism 6 adjoins theleft side of the bearing 31 b inner race. The anti-reverse mechanism 9adjoins the right side of the bearing 31 a inner race on the left end ofthe spool shaft 2. Further, the inside face of the side plate 10 abutsthe left end of the outer race. The spool 3 abuts on the left side ofthe outer race of the right-side bearing 32 b that supports the spool 3.Further, four disk springs 34 abut on the right side of the inner racevia a washer (not shown). The disk springs 34 are provided in order tomake the drag force adjustable over a broad range with respect to pivotof the brake operating lever (described below), without the drag forceelevating abruptly. A later described friction disk 36 in the lever-dragmechanism 7 via a return spring 47 abuts on the left side of the innerrace of the left bearing 32 a that supports the spool 3. The right sideof the outer race abuts on the spool 3.

The spool 3 has a bobbin trunk 3 a, and flanges 3 b that are formedintegrally with the bobbin trunk 3 a on either end. The spool-lockingmechanism 8, which allows the spool 3 to rotate in the line-retrievingdirection and locks it from rotating in the line-reel-out direction, isprovided outward of the flange 3 b on the right side (handle-mountingside) in FIG. 1. Further, a brake disk 35 for the lever-drag mechanism 7is mounted outward of the flange 3 b on the left side in FIG. 1. Theouter periphery of the left flange 3 b is formed into a cylindricalportion 3 d extending outward in the spool shaft direction, forattaching a cover 39 for covering the brake disk 35.

The handle 4, as shown in FIGS. 1 and 2, is fastened by a fixing screw60 to the projecting end of the cylindrical handle shaft 5, which isdisposed beneath the spool shaft 2, and parallels the spool shaft 2. Abrim 60 a is formed on the fixing screw 60. Twelve round-arcuatedepressions 60 b spaced at circumferential intervals are formed on thebrim 60 a, which is locked in place by a screw 61, the head of whichengages a recess 60 b. The handle shaft 5 is rotatively mounted in acylindrical member 15 a inserted into the bearing block 15 frontwardbelow the boss portion 11 a. A main gear 16 is mounted non-rotatably onthe tip of the handle shaft 5.

As shown in FIG. 1, the rotation transmission mechanism 6 includes: themain gear 16, which is carried rotatively by the handle shaft 5 forthe-handle 4; and the pinion gear 17, which is formed unitarily with thespool shaft 2. Rotation from the handle 4 is transmitted to the spoolshaft 2 via the handle shaft 5, the main gear 16, and the pinion gear17.

Lever-Drag Mechanism Configuration

The lever-drag mechanism 7 as shown in FIG. 1 includes: the brake disk35, which is mounted on the outside face of the FIG. 1 left-side flange3 b on the spool 3; the friction disk 36, for contacting the brake disk35; and the drag-shifting mechanism 38, which is for reciprocatinglyshifting the spool 3 and the friction disk 36 in the spool axialdirection.

The brake disk 35 is for example a washer-shaped disk member made ofstainless steel, and is mounted non-rotatably with respect to the spool3 on the outside face of the left-side flange 3 b on the spool 3 bymeans of a diametrically inward plurality of attaching screws 40disposed on the lateral surface and spaced at circumferential intervals.

The friction disk 36 is disposed opposing the brake disk 35. Aring-shaped friction plate 36 a made of abrasion-resistant material,e.g., carbon graphite or fiber-reinforced resin, is fastened to thesurface of the friction disk 36 that opposes the brake disk 35, by asuitable fastening means, such as screws. In the central portion of thefriction disk 36 is a cylindrical boss portion 36 b that protrudesaxially outward; and a pin 2 a, which is fitted into the spool shaft 2,passing through the spool shaft 2 diametrically, interlocks with theboss portion 36 b. Accordingly, the friction disk 36 is mounted on thespool shaft 2 non-rotatably, and rotates together with the spool shaft2. Further, a ratchet wheel 50 in the anti-reverse mechanism 9 isfitted, non-rotatably yet free to shift axially, to the FIG. 4 left-endsurface of the boss portion 36 b on the friction disk 36. Additionally,a cover member 39 covers the friction disk 36. Likewise, the bossportion 36 b on the friction disk 36 passes through the cover member 39and extends toward the bearing 31 a.

The cover member 39, a disk-shaped component in the center of which is athrough-hole 39 a through which the boss portion 36 b on the frictiondisk 36 passes, is fastened along its outer periphery to the cylindricalportion 3 d of the spool 3 by a plurality of bolts. As shown in FIG. 3,a seal member 65 is interposed between the through-hole 39 a in thecover member 39, and the boss portion 36 b on the friction disk 36, forpreventing liquids from invading through the clearance between them intothe interior. The through-hole 39 a has a larger-diameter relief face 39b situated axially outward, and disposed axially inward in proximitythereto, a smaller-diameter contact face 39 c.

The seal member 65 is fitted into a seal-attachment portion 36 cconsisting of an annular groove formed in the outer circumferentialsurface of the boss portion 36 b. The seal member 65 is a component madeof an elastic substance such as NBR, for example. The seal member 65includes: an elastic-manufacture cylindrical portion 65 a that can befit into the seal-attachment portion 36 c; and a sealing portion 65 bformed integrally with the cylindrical portion 65 a on its outercircumferential surface, tapered toward the inner circumferentialsurface of the through-hole 39 a, and whose distal edge is capable ofcontacting on the cover member 39. The cylindrical portion 65 a is aring-shaped section that is rectangular in cross-section; while thesealing portion 65 b is a section that extends diametrically from theouter circumferential surface of the cylindrical portion 65 a, towardthe through-hole 39 a. The tapered distal-edge part of the sealingportion 65 b is peaked, and can come into contact with the contact face39 c of the through-hole 39 a, whereas it cannot come into contact withthe relief face 39 b.

The outer diameter of the sealing portion 65 b is 8% or more, 50% orless of the outer diameter of the flanges 3 b of the spool 3, andpreferably is 10% or more, 20% or less. In this case, because the outerdiameter of the sealing portion 65 b is 50% or less than the outerdiameter of the flanges 3 b, the contacting surface area of the sealingportion 65 b is made sufficiently small with respect to the spool 3,which curbs degradation in rotational performance of the spool 3 thoughthe spool 3 is brought into contact with the seal member 65. Likewise,because the outer diameter of the sealing portion 65 b is 8% or more,the spool shaft 2 can have a large diameter. Therefore, even with a sealmember 65 fitted into the friction disk 36 mounted encompassing thespool shaft 2, the diameter of the spool shaft 2 will be large enough tosustain the strength of the spool shaft 2.

The distal edge of this sealing portion 65 b opposes the relief face 39b when the spool 3 is in the brake-release state—(portion downward fromthe spool center axis X in FIG. 3) situation—and is out of contact withthe cover member 39. Likewise, when in the braking state—(portion upwardfrom the spool center axis X in FIG. 3) situation—it opposes the contactface 39 c and contacts the through-hole 39 a in the cover member 39 toseal the clearance between the cover member 39 and the friction disk 36.

Sealing the inner portion of the cover member 39 with the seal member 65as such makes the friction disk unlikely to become water-wet, whichkeeps the drag performance from fluctuating. Likewise, the fact that thetapered sealing portion 65 b is brought into contact with the contactface 39 c to seal the clearance between the boss portion 36 b and thecover member 39 means that the surface area of the places in contact issmall, and that the rotational performance is unlikely to deteriorate.Moreover, since, like O-rings, the seal member 65 is entirely made of anelastic substance it is extendable/contractible, which means that it maybe fastened to the seal-attachment portion 36 c simply—just bystretching the cylindrical portion 65 a to fit it into the boss portion36 b, and shifting it axially. Components and space for fastening theseal member 65 are therefore made unnecessary.

The anti-reverse mechanism 9 is a ratchet-type one-way clutch thatincludes: a ratchet wheel, and a pair of ratchet pawls (not illustrated)whose tips interlock with the ratchet wheel 50, and which are disposedouter peripherally about the ratchet wheel 50. A spacer element 54 isfitted in between the ratchet wheel 50 and the bearing 31 a inner race,contacting the two.

The friction disk 36 cannot shift in the spool axially outward direction(FIG. 1 leftward), i.e., in the direction parting away from the brakedisk 35, and meanwhile it is permitted by the anti-reverse mechanism 9to rotate in the line-retrieving direction, but prohibited from rotatingin the line reel-out direction.

Herein, in the brake-released state as shown on the lower side of thespool axis X in FIG. 1, a gap opens between the friction plate 36 a onthe friction disk 36, and the brake disk 35; and in the braking state asshown on the upper side of the spool axis X in FIG. 1, the two adhere.The drag force is changed by adjusting the degree of adherence.

As shown in FIG. 1, the drag-shifting mechanism 38 includes: abrake-handling lever 45 provided pivotally on the reel unit 1; apressing mechanism 46, which, in response to pivoting the brake-handlinglever 45 clockwise in FIG. 2, presses against the spool 3 and the brakedisk 35 and shifts them FIG. 3 leftward; and a return spring 47, whichis disposed between the friction disk 36 and the spool 3, and shifts thespool 3 rightward in FIG. 1 in response to the brake-handling lever 45moving FIG. 2 counterclockwise.

The brake-handling lever 45 is mounted to the reel unit 1 free to pivotbetween the brake release position, indicated by solid lines in FIG. 2,and the maximum braking position, indicated by phantom lines. Thebrake-handling lever 45 includes a lever portion 45 a that is pivotallymounted to the boss portion 11 a, and a knob portion 45 b that isfastened to the fore end of the lever portion 45 a. The basal end of thelever portion 45 a interlocks non-rotatably with the pressing mechanism46.

Lever-Drag Mechanism Operation

The following explains the braking function of the lever drag mechanism7.

In the lever drag mechanism 7, when the brake handling lever 45 ispivoted from the braking position, indicated by phantom lines in FIG. 2,into the brake release position, indicated by solid lines, the stateshown above is switched into the state shown on the lower side of thespool axis X in FIG. 1. Initially the spool 3 is pressed by the urgingforce of the return spring 47 and shifted FIG. 1 rightward. A gapthereby opens between the brake disk 35 and the friction disk 36. Thespool 3 is further pressed via the bearing 32 a and shifted rightward.This releases the braking on the spool 3. Meanwhile when the spool 3shifts, the pressing mechanism 46 is pressed via the bearing 32 b, thedisk springs 34, the pinion gear 17, and the bearing 31 b, and retreatsFIG. 1 rightward. Then, when the brake-handling lever 45 is pivoted intothe brake release position, there is a shift into the state shown on thelower side of the spool axis X in FIG. 1. This consequently brings thesealing portion 65 b of the seal member 65 opposite the relief face 39b, as shown on the lower side of the spool axis X in FIG. 1, whererotational resistance due to the seal member 65 when the spool 3 is inits free-rotation state will not arise, which lets the line pay outsmoothly from the spool 3 so that the fishing line reel outs agilely.

On the other hand, when the brake handling lever 45 is pivoted from thebrake release position indicated by solid lines in FIG. 2, into thebraking position indicated by phantom lines, the state shown on thelower side is switched into the state shown on the upper side of thespool axis X in FIG. 1. Initially, pivoting the brake handling lever 45shifts the pressing mechanism 46 leftward in the spool axial direction.This presses on and shifts the outer race of the bearing 31 b, and thespool 3 is pressed via the pinion gear 17, the disk springs 34, and thebearing 32 b and shifted leftward in the spool axial direction (FIG. 1leftward). Consequently, the brake disk 35 also shifts leftward axially,whereby the brake disk 35 is brought near the friction disk 36. Then,when the brake disk 35 comes into contact with the friction disk 36,which is axially immovable and non-rotatable in the line reel-outdirection, drag force acts on the spool 3. When the brake handling lever45 is then pivoted to the maximum pivotal position, pressing force ismaximized and the friction disk 36 pressing on the brake disk 35 yieldslarge drag force. In this situation, as shown on the upper side of thespool axis X in FIG. 3, the sealing portion 65 b of the seal member 65is brought opposite and into contact with the contact face 39 c wherebythe seal member 65 when the spool 3 is in the braking state seals theclearance securely to lessen fluctuations in drag performance. What ismore, the fact that the surface area in which the distal edge of thesealing portion 65 b contacts the contact face 39 c is small meanslittle increase in rotational resistance, so that rotational performanceis unlikely to be impaired.

Meanwhile, when a fish is caught on the terminal tackle and the spool 3spins in the line reel-out direction, the ratchet wheel 50 is prohibitedfrom rotating in the line reeling-out direction. Consequently thefriction disk 36 is prevented from rotating in the line reeling-outdirection, and the set drag force acts on the spool 3.

Embodiment 2

Overall Configuration

In the foregoing Embodiment 1, an embodiment in which a sealingstructure having to do with the present invention is adopted in alever-drag type dual-bearing reel was illustrated, but herein anembodiment in which it is adopted in a spinning reel will be explained.

Set out in FIG. 4, a spinning reel in which a second embodiment of thepresent invention is adopted is furnished with: a reel unit 102 that ismountable on a fishing rod, a handle assembly 101 that fits rotativelyonto the reel unit 102 about left/right shafts, a rotor 103, and a spool104. The rotor 103 rotates linked to rotation of the handle assembly101, wherein it guides fishing line onto the spool 104, and isrotatively carried on the front of the reel unit 103, turning about afront-to-rear axis. The spool 104 is for winding fishing line guided bythe rotor 103 onto its outer circumferential surface, and is disposed onthe front of the rotor 103, where it is let shift reciprocatingly in thefront-to-rear axial direction.

Reel Unit Configuration

As shown in FIG. 6, the reel unit 102 includes: a reel body 2 aconstituting the main portion of the reel unit 102 and in the side ofwhich is an opening 102 c; a T-shaped rod-attachment leg 102 b integralwith and extending diagonally upward and forward from the reel body 102a; and a cover member 102 d that is screwed fast onto reel body 2 a toshut the opening 102 c.

The reel body 102 a in the interior has a mechanism-mounting spaceranging to the opening 102 c. Provided in the space are, as shown inFIG. 5: a rotor drive mechanism 105 that, linked to rotation of thehandle assembly 101, rotates the rotor 103; and an oscillating mechanism106 that pumps the spool 104 back and forth to wind on fishing lineuniformly.

As shown in FIG. 6, a first flange portion 102 e, and a cylindricalportion 102 f projecting forward from the first flange portion 102 e areformed on the front of the reel body 102 a. The first flange portion 102e has an approximately semicircular contour as though missing a sectionconsisting of a chord and a circular arc, and is formed standing on thefront end of the aperture 102 c. The cylindrical portion 102 f is acircular cylindrical section in the interior of which is mounted, asshown in FIG. 5, a one-way clutch 151 to an anti-reverse mechanism 150for prohibiting/releasing rotation (reversal) of the rotor 103 in theline reel-out direction. A channel portion 102 h, D-shaped viewed incross-section, is formed on the rear end, at a slightly smaller diameterthan the rest, of the cylindrical portion 102 f; and the area on therear face of the channel portion 102 h where the cover member 102 d ismounted communicates with and opens onto the aperture 102 c.

A second flange portion 102 g that is shaped into an approximatelysemicircular contour consisting of the chord and circular arc from themissing section of the first flange portion 102 e is formed at the frontend of the cover member 102 d. A waterproofing seal 181 made from anelastic substance is fitted into the surface of the second flangeportion 102 g where it contacts the first flange portion 102 e and therear surface of the cylindrical portion 102 f, for sealing the gapstherewith. The waterproofing seal 181 is formed into a band shape in anapproximately semicircular arc that extends from the front surface tothe rear surface of the second flange portion 102 g, and continues inlocations opposite the surface where the second flange portion 102 gcontacts the first flange portion 102 e and the surface where itcontacts the rear face of the channel portion 102 h. The waterproofingseal 181 is fitted into an approximately semicircular arcuate mountinggroove 181 a formed on the front face of the second flange portion 102g.

As shown in FIG. 7, a cylindrical boss portion 117 a is formed on theright lateral surface of the reel body 102 a. The boss portion 117 a isformed protruding in/outward from the reel body 102 a, for accommodatinga bearing 116 a that carries the right end of a master gear shaft 110. Aboss portion 117 b is formed in a position on the cover member 102 dopposing the boss portion 117 a. The boss portion 117 b is formedprojecting in/outward from the reel body 102 a, for accommodating abearing 116 b that carries the left end of the master gear shaft 110.The boss portion that is opposite the side in which the handle 101 isfitted (the boss portion 117 a in FIG. 7) is closed off by a waterproofcap 119. The waterproof cap 119 is a cylindrical cover having a base,and is fastened by screw-joining into the inner circumferential surfaceof either one of the boss portions 117 a, 117 b.

As shown in FIGS. 5 and 6, the rear of the reel unit 102 is covered by aprotective cap 113 manufactured from, e.g., metal or a synthetic resin.The protective cap 113 is disposed to cover the reel unit 102 lower partand back surface, extending from beneath the reel body 102 a and thecover member 102 d across the back surface and further to therod-mounting leg 102 b. The protective cover 113 isremovably/reattachably fastened to the reel unit 102 by screws. A spacer113 a made of a synthetic resin intervenes between the protective cover113 and the reel unit 102. The spacer 113 a is interposed to fill thegap between the protective cover 113 and the reel unit 102. Byinterposing a spacer 113 a as such, though the protective cover 113 ismanufactured from a synthetic resin, variations in the gap owing todiscrepancies in its manufacture are absorbed.

Handle Assembly Configuration

The handle assembly 101 is a component that, as shown in FIG. 7, isdetachably/reattachably fitted to the master gear shaft 110, andincludes: a handle body 107, a grip portion 108 (see FIG. 5), and a sealmember 109 fitted onto the handle body 107. The handle assembly 101 isattachable to the reel body 102 on either the right side (FIG. 4) or theleft side (FIG. 5). The handle body 107 includes an mounting portion 107a fitted non-rotatably, detachably/reattachably to the master gear shaft110, and an arm portion 107 b that extends from the fore end of themounting portion 107 a in a direction intersecting the master gear shaft110.

The mounting portion 107 a includes: a handle shaft portion 107 c,rectangular in cross section, that engages into a engagement hole 110 a,rectangular in cross section, formed in the center of the master gearshaft 110; a flange portion 107 d into which the handle shaft portion107 c is inserted, and with which it is thereby formed unitarily; and ashaft-collar portion 107 e that is screwed into the flange portion 107d. A threaded hole 107 f is cut in the distal end of the handle shaftportion 107 c; and through the side opposite the end inserted into themaster gear shaft 110, the handle body 107 is non-rotatably fastened tothe master gear shaft 110 by screwing a fixing screw 118 into thethreaded hole 107 f. A seal-attachment portion 107 g consisting of anannular groove is formed in the flange portion 107 d in a location thatallows it to oppose the inner circumferential surfaces 117 c or 117 d,of the boss portion 117 a on the reel body 102 a, or the boss portion117 b on the cover member 102 d. The shaft-collar portion 107 e isdisposed so as to cover handle shaft portion 107 c from without.

The arm 107 b is collapsibly fitted to the fore end of the mountingportion 107 a. The arm 107 b is bent mid-course, where it extends in adirection that intersects the master gear shaft 110, and the gripportion 108 is fitted to its extended tip.

The grip portion 108 includes a grip shaft (not illustrated)crimp-fastened to the fore end of the arm 107 b, and a T-shaped griprotatively fitted onto the grip shaft.

The seal member 109 is for contacting on the inner circumferentialsurface of the boss portion 117 a or 117 b to seal the clearance betweenthe boss portion 117 a or 117 b and the mounting portion 107 a, and ismade of an elastic substance such as NBR, for example. The seal member109 is fitted detachably/reattachably to the mounting portion 107 a. Byfitting on this seal member 109, liquids may be prevented from invadinginto the bearing 116 a or 116 b.

The seal member 109, as shown in FIG. 8, has a cylindrical portion 109a, rectangular in cross-section, that fits into the seal-attachmentportion 107 g, and a sealing portion 109 b that extends diametricallyoutward from the cylindrical portion 109 a. The sealing portion 109 b,whose distal edge pointedly tapers toward the inner circumferentialsurface of the boss portion 117 a or 117 b, is formed integrally withthe cylindrical portion 109 a. The part of the sealing portion 109 bthat contacts the inner circumferential surface is inclined headingoutward of the reel body 102.

With the handle assembly 101 structured in this way, the handle assembly101 is inserted into the engagement hole 110 a, with the waterproof cap119 taken off, through either the left/right of the master gear shaft110. And by screwing in the fixing screw 118 through the end oppositethe insertion side, the handle assembly 101 can be mounted on the mastergear shaft 110 through either the left/right. When mounted, attachingthe waterproof cap 119 to the boss portion on the side opposite themounting side prevents liquids from invading interiorly from the sideopposite; and on the mounting side moreover, the seal member 109prevents liquids from invading interiorly. The exteriors of both thebearings 116 a, 116 b may therefore be sealed by the single seal member109, which prevents liquids from invading into the master gear shaft 110by a simple configuration without increasing the width of the reel unit102.

Likewise, the fact the seal member 109 is fitted into theseal-attachment portion 107 g consisting of an annular groove, enablespreventing movement of the seal member 109 in the axial direction,without providing separate components and extra space. Further, the factthat the seal member 109 is made of an elastic substance lets it be fitinto the seal-attachment portion 107 g simply, by sliding the sealmember 109 axially after it is fitted stretched like an O-ring onto theflange portion 107 d. Moreover, the fact that the distal edge part ofthe sealing portion 109 b that contacts the inner circumferentialsurfaces 117 c, 117 d of the boss portions 117 a, 117 b is tapered to apeak means that the resistance in contact with the inner circumferentialsurface 117 c, 117 d is small, which, by curbing increase in rotationalresistance on the handle assembly 101, controls degradation inrotational performance. Likewise, because the sealing portion 109 b fromthe very first is inclined heading outward, it will not become bent overbackwards in fitting the handle assembly 101 into the master gear shaft110 through the outer side of the reel unit 102. The handle assembly 101may therefore be mounted into the master gear shaft 110 smoothly.Moreover, the fact that the contacting part of the sealing portion 109 bis inclined heading outward, means that liquids are less likely toinvade interiorly.

Rotor-Drive Mechanism Configuration

As shown in FIG. 5, the rotor drive mechanism includes a master gear 11into which the handle assembly 101 is non-rotatably fitted, and a piniongear 112 that meshes with the master gear 111.

The master gear 111 is a face gear, and is formed unitarily with themaster-gear shaft 110. The master-gear shaft 110 is a hollow componentmade of, e.g., stainless steel, through the center of which theengagement hole 110 a is formed; and either end thereof is rotativelysupported via the bearings 116 a, 116 b in the reel body 102 a and thelid member 102 d.

The pinion gear 112, a cylindrical component, as shown in FIG. 5 isdisposed running in the front-to-rear direction, and is fittedrotatively in the reel body 102 a. The front portion 112 a of the piniongear 112 penetrates the center part of the rotor 103, and is fastened tothe rotor 103 in the penetrated part by a nut 133. The pinion gear 112is rotatively supported at the mid-portion and rear end in the axialdirection via respective bearings 114 a, 114 b in the reel body 102 a. Aspool shaft 115 passes through the interior of the pinion gear 112.Along with meshing with the master gear 111, the pinion gear 112 alsomeshes with the oscillation mechanism 106.

Rotor Configuration

The rotor 103 includes a round cylinder portion 130 fastened to thepinion gear 112; first and second rotor arms 131, 132 opposing eachother provided sideways on the round cylinder portion 130; and a bailarm 140 that guides fishing line onto the spool 104. The round cylinderportion 130 and the two rotor arms 131, 132 are, e.g., aluminum-alloymanufactured, and are formed unitarily.

As shown in FIG. 9, a front wall 141 is formed on the front of the roundcylinder portion 130, and a rearward-projecting boss 142 is formed inthe center portion of the front wall 141. A through-hole into which thepinion gear 112 is non-rotatably interlocked is formed in the center ofthe boss 142; the front portion 112 a of the pinion gear 112 and thespool shaft. 115 penetrate the through-hole. An inertia-imparting ring144 for imparting inertia to the rotor 103 is detachably/reattachablyfitted onto the front face of the front wall 141 by screws (notillustrated). The inertia-imparting ring 144 is provided to regulate thechange in rotational feel that goes along with lightening the weight ofthe rotor 103.

The nut 133 is screw-joined to the front portion 112 a of the piniongear 112, and thus the rotor 103 is fastened non-rotatably to the foreend of the pinion gear 12 by the nut 33. A bearing 135 is disposed alongthe inner periphery of the nut 133. The bearing 135 is furnished tosecure the clearance between the spool shaft 115 and the inner surfaceof the pinion gear 112. A seal member 136 having a lip along its innerperiphery is fitted onto the front face of the nut 133 and the bearing135. The distal edge of the seal member 136 contacts on the spool shaft115. This prevents liquids from permeating into the interior of the reelunit 102 from the spool shaft 15.

The aforementioned anti-reverse mechanism 150 is disposed neighboringthe boss 142. As shown in FIG. 5, the anti-reverse mechanism 150includes the one-way clutch 151, and a switching mechanism 152 thatswitches the one-way clutch 51 between an actuated state(reverse-prohibited state) and an non-actuated state (reverse-permittedstate).

The inner race 151 a of the one-way clutch 151, a roller-type one-wayclutch whose inner race is free-rotating, is fitted non-rotatably to thepinion gear 112, and the outer race 151 b is fitted non-rotatably intothe cylindrical portion 102 f. A spacer 143 made of stainless steelalloy interposes between the inner race 151 a and the boss 142 on therotor 103, as shown in FIG. 9. The spacer 143 is a thin roundcylindrical component having a cylinder portion 143 a and a disk portion143 b; the cylinder portion 143 a is fit onto the outer periphery of theboss 142, while the disk portion 143 b is sandwiched between thefront-end face of the inner race 151 a and the boss 142.

In the cylindrical portion 102 f interior, a shaft seal 185 having a lipis fitted frontward of the one-way clutch 151. The distal-edge lip ofthe shaft seal 185 contacts the outer peripheral surface of the cylinderportion 43 a of the spacer 143. Herein, liquids are not likely to invadealong the inner periphery of the spacer 143, because the disk portion143 b is sandwiched between the boss 142 and the inner race 151 a.Accordingly, sealing the outer circumferential surface of the spacer 143keeps liquids from invading the interior of the cylindrical portion 102f. Herein, once the spacer 143 is installed, if the rotor 103 is notcentered correctly, when the shaft seal 185 is brought directly intocontact with the boss 142 while fastening the rotor 103 to the piniongear 112, the shaft seal 185 will not form a good seal with the spacer143. Thus, mounting the spacer 143 and centering it with the shaft seal185 in advance stabilizes the sealing ability of the shaft seal 185.

As shown in FIG. 5, the switching mechanism 152 has a stopper shaft 153.The stopper shaft 153 is mounted on the reel body 102 a to let it pivotbetween a non-operational posture and an operational posture. Thestopper shaft 153 includes: a stopper knob 153 a that passes through andprojects rearward from the reel body 102 a and the protective cap 113 sothat it may be operated; a shaft portion 153 b fixed to the stopper knob153 a; and a cam 153 c fixed to the tip of the shaft 153 b.

As shown in FIG. 6, the stopper knob 153 a is removably/reattachablyfixed to the shaft 153 b by means of an Allen set-screw 158. Herein, thestopper knob 153 a is made removable from/reattachable to the shaft 153b because the stopper knob 153 a must be taken off when the protectivecap 113 is taken off in order to undo the lid member 102 d. Using theAllen set-screw 158 for fastening the stopper knob 153 a keeps fishingline from getting caught, without sinking the screw head in a holebecause the screw has no head. Because the Allen set-screw 158 has nohead, using the screw for fastening the stopper knob 153 a means thatfishing-line snags may be made unlikely without sinking the screw headin a hole.

The cam 153 c is toggle-urged between the non-operational posture andthe operational posture by means of a toggle-spring mechanism 159. Thetip of the cam 153 c engages with the one-way clutch 151, and isconfigured such that the one-way clutch 151 is switched betweennon-operational posture and an operational posture by the stopper shaft153 pivoting.

Oscillating Mechanism Configuration

The oscillating mechanism 106, as shown in FIGS. 5 and 7, has a worm 121disposed approximately directly beneath and parallel to the spool shaft115, a slider 122 that reciprocates along the worm 121, and anintermediate gear 123 fixed to the fore end of the threaded shaft 121.The slider 122 is movably supported on two guide shafts 124 that aredisposed in parallel with the worm 21. The hind end of the spool shaft115 is non-rotatably fixed to the slider 122. The intermediate gear 123meshes with the pinion gear 112 via a (not illustrated) gear-down train.

Spool Configuration

The spool 104 has, as shown in FIG. 5, a shallow-channel contour, and isdisposed between the first rotor arm 131 and the second rotor arm 132 ofthe rotor 103. The spool 104 is linked to the fore end of the spoolshaft 115 via a drag mechanism 160. The spool 104 includes: a bobbintrunk 104 a circumferentially onto which fishing line is wound; a skirt104 b that is integrally formed on the rear of the bobbin trunk 104 a;and a flange 104 c established on the front end of the bobbin trunk 104a.

The bobbin trunk 104 a is an approximately dual-stage drum member havinga boss in the center, and the encompassing outer circumferential surfaceof the drum section constitutes a peripheral surface that parallels thespool shaft 115. The bobbin trunk 104 a is mounted, as shown in FIG. 9,rotatively to the spool shaft 115 on two bearings 156, 157 into theboss. The skirt 104 b, a round cylindrical component having a base,flares diametrically from the rear end portion of the bobbin trunk 104a, then extends rearward. The front flange 104 c includes: a standingportion 104 d integrally formed diametrically outward from the front endportion of the bobbin trunk 104 a; and a ring portion 104 e made ofmetal or ceramic removably/reattachably mounted on the standing portion104 d. The ring portion 104 e is affixed to the standing portion 104 dby means of a flange-fastening member 104 f that is screwed into theinner circumferential surface of the bobbin trunk 104 a.

The position of the spool 104 is set by abutting on a locating washer154 that is fitted to the spool shaft 115.

Drag Mechanism Configuration

The drag mechanism 160 is mounted between the spool 104 and the spoolshaft 115, and is a device for applying drag force to the spool 104. Thedrag mechanism 160 has, as shown in FIG. 9: a knob unit 161 foradjusting the drag force by hand; and a friction unit 162 made up of aplurality of disks that are pressed toward the spool 104 by means of theknob unit 161.

The knob unit 161 includes: a first member 163 installed non-rotatablyyet axially movably on the chamfers 115 a; a second member 164 disposedaxially frontward of the first member 163 and screwed onto the spoolshaft 115; and a sounding mechanism 165 fitted in between the firstmember 163 and the second member 164.

The first member 163 is a round cylindrical member having a brim, andincludes a cylinder portion 163 a and a ring-shaped brim portion 163 blarger in diameter than the cylinder portion 163 a. A flat-sided keyway166 into which the spool shaft 115 non-rotatably interlocks is formed inthe inner margin of the cylinder portion 163 a. The rear end face on thecylinder portion 163 a of the first member 163 abuts on the frictionunit 162. A sealing washer 171 for preventing liquids from invadingtoward the friction unit 162 from without is fitted between the cylinderportion 163 a of the first member 163 and, along the inside of thebobbin trunk 14 a, the drum section inner circumferential surface. Thesealing washer 171 is a sealing component having a lip on the outerperiphery and obtained, e.g., by “outsert”—molding a plate-shapedelastic element made of NBR onto the circumferential perimeter of ringelement made of stainless steel. The sealing washer 171 is urged FIG. 8leftward by a snap ring 179. A ring-shaped protrusion 171 c is formed onthe FIG. 9 left-hand face of the sealing washer 171. This protrusion 171c abuts a later-described cover member 168 to prevent liquids frominvading along the inner margin.

The second member 164 is installed opposing the first member 163, and isrotatable relative to the first member 163. The second member 164includes: a knob body 167 disposed aligned frontward of the firstcomponent 163 in the spool shaft 115 direction; and the cover member168, whose fore end is fixed to the outer periphery of the knob body167, and in the interior of which the first component 163 is reltaivelyrotatably housed.

The knob body 167 is a saucer-shaped component, the front surface ofwhich forms a forward projecting, roughly trapezoidal knob 167 a. A nut169 that screws-join into the fore end of the spool shaft 115 is fittednon-rotatably yet axially movably in the interior of the knob body 167.Further, a coil spring 170 is disposed in the compressed state about theouter periphery of the spool shaft 115 in the interval between thesecond member 164 and the nut 169.

The cover member 168 is a cylindrical component having a stepped base,through which base the round cylinder portion 163 a of the firstcomponent 163 passes. Further, the protrusion 171 c on the sealingwasher 171 abuts on the base. A cylinder portion 168 a of the covermember 168 is screw-stopped onto the outer circumferential surface ofthe knob body 167.

An O-ring 173 is fitted in between the knob body 167 and the fore end ofthe cylinder portion 168 a of the cover member 168. The O-ring 173 is anelastic element made, e.g., of NBR, and is provided in order to preventliquids from invading the interior from the clearance between the firstcomponent 163 and the knob body 167 of the second member 164. As far asliquids invading through this clearance is concerned: It could happenfor example that though the sealing washer 171 is provided, water mightencroach through the clearance between the first component 163 and thespool shaft 115 and as far as the friction unit 162. The frictionportion 162 might then get wet, altering the drag force.

The friction unit 162 includes a disk 191 that contacts the firstcomponent 163, and a drag sounding mechanism 193 fitted to the firstdisk 191. The first disk 191 has: an inner disk portion 191 a; acircular cylinder portion 191 b that extends rearward from thecircumferential periphery of the inner disk portion 191 a; and an outerdisk portion 191 c that extends diametrically outward from the rear endof the circular cylinder portion 191 b. By interlocking the spool shaft15 into the inner disk portion 191 a, the first disk 191 isnon-rotatable with respect to the spool shaft 115. Furthermore, the dragsounding mechanism 193 is fitted to the outer disk portion 191 c, andmeanwhile is contiguous with the spool 104 via drag disks 192 made ofgraphite. When the spool shaft 15 and the spool 104 are relativelyrotatable, i.e., during drag operation, the drag sounding mechanism 193issues sound.

Reel Handling and Operation

With this spinning reel, when the line is to be reeled out duringcasting or the like, the bail arm 140 is flipped over into theline-releasing posture. Consequently, the fishing line is reeled outsuccessively from the leading-edge side of the spool 104 by the terminaltackle under its own weight.

During line retrieval, the bail arm 140 is returned into theline-retrieving posture. This automatically takes place by the operationof a not-illustrated bail-flipping mechanism when the handle assembly101 is rotated in the line-retrieving direction. The handle assembly 101torque is transmitted to the pinion gear 112 via the master-gear shaft110 and the master gear 111. The torque transmitted to the pinion gear112 is transmitted from its front portion 112 a to the rotor 103, andmeanwhile is transmitted via the gear-down train to the oscillatingmechanism 106 by the intermediate gear 123 that meshes with the piniongear 112. Consequently, along with the rotor 103 rotating in theline-retrieving direction, the spool 104 pumps back and forth.

In the course of fishing, there are times when waves splash on the reeland the reel gets wet. Because the sealing washer 171 and the O-ring 173are fitted in the drag mechanism 160, water is not apt to encroach fromthe front or rear to the friction unit 162. Therefore, once the dragforce is adjusted, fluctuations in the drag force due to water soakingin will be scarce.

Furthermore, furnishing the seal member 109 in the handle assembly 101clearance with the reel body 102 a, and furnishing the waterproofingseal 181 between the reel body 102 a and the cover member 102 d preventsliquids from invading into the interior mechanism-mounting space. Thiskeeps seawater and the like from entering the interior, making itunlikely that crystalline deposits of salt will form on the gears, guidesections and inside the bearings.

Other Embodiments

(a) The foregoing Embodiment 1 was illustrated as an example in alever-drag type dual-bearing reel, and the foregoing Embodiment 2 wasillustrated as an example in a front-drag type spinning reel; but thepresent invention may be applied to all seal structures employed infishing reels, such as: star-drag type dual-bearing reels, or rear-dragtype spinning reels, or spinning reels not having a drag, or lever-dragtype spinning reels.

(b) In the foregoing embodiment, NBR was exemplified as a seal-membermaterial, but “an elastic substance” is not limited to NBR, and includesall elastic substances, such as silicone rubber, styrene rubber, andnatural rubber.

(c) In the foregoing embodiment, the handle assembly 101 structured tobe fastened to the master gear shaft 110 by means of the fixing screw118 was exemplified, but the present invention may be applied also to ahandle assembly structured to fasten by screwing into the master gearshaft 110.

Effects of Invention

In accordance with the present invention, the fact that the taperedsealing portion is brought into contact with the second member to sealthe clearance between the two members makes the surface area of thecontacting part small, making degradation in rotational performanceunlikely. Likewise, the fact that like an O-ring the entire seal memberis made of an elastic substance makes it extendable/contractible, sothat it may be fastened to the first member simply—merely by fitting thecylindrical portion into a groove, for example. Components and space forfastening the seal member are therefore made unnecessary.

The terms of degree such as “substantially”, “about” and “approximately”as used herein mean a reasonable amount of deviation of the modifiedterm such that the end result is not significantly changed. These termsshould be construed as including a deviation of at least ±5% of themodified term if this deviation would not negate the meaning of the wordit modifies.

While only selected embodiments have been chosen to illustrate thepresent invention, it will be apparent to those skilled in the art fromthis disclosure that various changes and modifications can be madeherein without departing from the scope of the invention as defined inthe appended claims. Furthermore, the foregoing description of theembodiments according to the present invention are provided forillustration only, and not for the purpose of limiting the invention asdefined by the appended claims and their equivalents.

1. A sealing structure for a fishing reel having a reel unit, a spoolshaft rotatively fitted in the reel unit, and a spool supportedrotatively on the spool shaft, said sealing structure comprising: afirst member non-rotatably mounted on the spool shaft; a second membernon-rotatably attached to the spool and having an inner peripheralsurface disposed about an outer peripheral surface of said first member,said second member being rotatable relative to said first member, saidsecond member having a small-diameter contact face and a large-diameterrelief face, said smaller-diameter contact face being closer to thespool than said large-diameter relief face is; and a seal member forsealing a clearance between said first member and said second member,and having a cylindrical portion made of an elastic substance andmountable on said first member, and a sealing portion formed integrallyon an outer circumferential surface of said cylindrical portion andtapering toward said inner peripheral surface of said second member suchthat a distal edge of said sealing portion can contact saidsmall-diameter contact face of said second member said sealing portionincluding a lip portion that can contact said small-diameter contactface of said second member.
 2. The sealing structure for a fishing reelset forth in claim 1, wherein said first member has an annular grooveformed in said outer circumferential surface opposing said secondmember, and said cylindrical portion is fitted into said annular groove.3. The sealing structure for a fishing reel set forth in claim 1,wherein: the fishing reel is a lever-drag-type dual-bearing reel havinga lever-drag mechanism and a line-winding spool, said first member is astationary component of the lever-drag mechanism in the fishing reel,said stationary component being immovable in an axial direction of thespool; and said second member is a movable component of the lever-dragmechanism, said movable component being rotatable relative to said firstmember and shiftable in the axial direction of the spool.
 4. The sealingstructure for a fishing reel set forth in claim 3, wherein said firstmember is a drag disk capable of braking the spool, and rotates linkedto a spool shaft passing through a center of the spool, and said secondmember is a cover member for covering said drag disk, and rotates linkedto the spool and meanwhile shifts in the axial direction together withthe spool and the spool shaft.
 5. The sealing structure for a fishingreel set forth in claim 4, wherein said drag disk has a boss portionpassing centrally through said cover member, said seal member is fittedto said boss portion, and said contact face and said relief face arearranged next to each other in the axial direction of the spool.
 6. Thesealing structure for a fishing reel set forth in claim 4, wherein saidsealing portion of said seal member parts away from said contact face ofsaid cover member and opposes said relief face when said drag disk inits brake-release state parts away from the spool, and comes intocontact with said contact face when said drag disk in its braking statecontacts the spool.
 7. The sealing structure for a fishing reel setforth in claim 3, wherein the spool has a bobbin-trunk portion andflange portions arranged on either end of the bobbin-trunk portion, anda size of said sealing portion in its outer diameter is 8% or more and50% or less of an outer diameter of the flange portions.
 8. A fishingreel, comprising: a reel unit; a spool shaft rotatively fitted in acentral portion of said reel unit; a spool carried rotatively on saidspool shaft; a handle disposed sideways on said reel unit; a firstmember non-rotatably coupled to said spool shaft of said fishing reel; asecond member non-rotatably attached to said spool and having an innerperipheral surface disposed about an outer peripheral surface of saidfirst member, said second member being rotatable relative to said firstmember, said second member having a small-diameter contact face and alarge-diameter relief face, said smaller-diameter contact face beingcloser to said spool than said large-diameter relief face is; and a sealmember for sealing a clearance between said first member and said secondmember, and having a cylindrical portion made of an elastic substanceand mountable on said first member, and a sealing portion formedintegrally on an outer circumferential surface of said cylindricalportion and tapering toward said inner peripheral surface of said secondmember such that a distal edge of said sealing portion can contact saidsmall-diameter contact face of said second member, said sealing portionincluding a lip portion that can contact said small-diameter contactface of said second member.
 9. The fishing reel set forth in claim 8,wherein said first member has an annular groove formed in said outercircumferential surface opposing said second member, and saidcylindrical portion is fitted into said annular groove.
 10. The fishingreel set forth in claim 8, wherein: said fishing reel is a lever-dragtype dual-bearing reel having a lever-drag mechanism, said first memberis a stationary component of said lever-drag mechanism, said stationarycomponent being immovable in an axial direction of said spool; and saidsecond member is a movable component of the lever-drag mechanism, saidmovable component being rotatable relative to said first member andshiftable in the axial direction of said spool.
 11. The fishing reel setforth in claim 10, wherein: said first member is a drag disk capable ofbraking said spool, and rotates linked to said spool shaft passingthrough a center of said spool; and said second member is a cover memberfor covering said drag disk, and rotates linked to said spool andmeanwhile shifts in the axial direction of said spool together with saidspool and said spool shaft.
 12. The fishing reel set forth in claim 11,wherein: said drag disk has a boss portion passing centrally throughsaid cover member; said seal member is fitted to said boss portion; andsaid contact face and said relief face are arranged next to each otherin the axial direction of said spool.
 13. The fishing reel set forth inclaim 11, wherein said sealing portion of said seal member parts awayfrom said contact face of said cover member and opposes said relief facewhen said drag disk in its brake-release state parts away from saidspool, and comes into contact with said contact face when said drag diskin its braking state contacts said spool.
 14. The fishing reel set forthin claim 10, wherein: said spool has a bobbin-trunk portion and flangeportions arranged on either end of said bobbin-trunk portion; and a sizeof said sealing portion in outer diameter is 8% or more and 50% or lessof an outer diameter of said flange portions.